Spindle motor and disk drive utilizing the spindle motor

ABSTRACT

Low-profile spindle motor whose entire shaft length is utilized to configure, along an encompassing sleeve, a radial dynamic-pressure bearing section. One end of the shaft is unitary with the rotor, and a cover member closes the other end. Between the sleeve upper-end face and the rotor undersurface a thrust bearing section is configured. Micro-gaps are formed continuing between the sleeve upper-end face and the rotor undersurface; the sleeve inner-circumferential surface and the shaft outer-circumferential surface; and the cover member inner face and the shaft end face, where an axial support section is established. Oil continuously fills the micro-gaps, configuring a full-fill hydrodynamic bearing structure. Hydrodynamic pressure-generating grooves in the radial bearing section are configured either so that no axial flow, or so that a unidirectional flow that recirculates from one to the other axial end of the radial bearing section through a communicating pathway is induced in the oil.

BACKGROUND OF INVENTION

[0001] 1. Technical Field

[0002] The present invention relates to spindle motors and disk-drivedevices utilizing the spindle motors; in particular to low-profilespindle motors furnished with hydrodynamic bearings, and to disk-drivedevices utilizing the spindle motors.

[0003] 2. Description of Related Art

[0004] In hard-disk drives that drive hard disks and like recordingdisks, spindle motors utilizing hydrodynamic bearings that, in order tosupport the shaft and sleeve as either one rotates relative to theother, employ the fluid pressure of a lubricating fluid such as oilinterposed between the two are known.

[0005] With regard to spindle motors utilizing hydrodynamic bearings ofthis sort, the applicant in the present application has proposed, inJapanese Laid-Open Pat. App. No. 2000-113582, a spindle motor asillustrated in FIG. 1. Between the bottom face of a rotor 100 and thetop-end face of a sleeve 102 in the spindle motor depicted in FIG. 1, athrust bearing section 104 is configured. Likewise, between the outercircumferential surface of a shaft 106 furnished integrally with therotor 100, and the inner circumferential surface of the sleeve 102,radial bearing sections 108, 108 are configured. The thrust bearingsection 104 generates lifting force on the rotor 100, and the radialbearing sections 108, 108 function to center-balance in the radialdirection, and prevent wobble in, the rotor 100.

[0006] The spindle motor depicted in FIG. 1 makes the thrust plate thatwould be a component of the thrust bearing in conventional hydrodynamicbearings unnecessary. The consequent advantage is a simplified structurethat reduces the cost of the motor and at the same time enables it to beslimmed, without appreciably compromising the bearing rigidity.Nevertheless, with the advent of the application of disk drives inminiature devices such as portable information terminals, demands are onthe rise to make the spindle motors used in the disk drives evenslimmer. In addition, calls for lowering the cost of spindle motorsstill further have gone hand in hand with reducing the cost of diskdrives.

[0007] Running counter to this is the fact that in its sleeve 102 thespindle motor depicted in FIG. 1 is provided with a communicatingpassage 110 made up of a through-hole 110 a and channels 110 b, 110 c.The communicating passage 110 brings outside air into the bearingareas—that is, it enables air to circulate into and out of the bearingareas—and thus would expose the end portions of the radial bearingsections 108, 108 to the air. Due to the pumping action ofdynamic-pressure-generating grooves formed in each bearing section,areas in which the internal pressure of the oil retained among thebearing sections becomes negative, i.e., at pressure less thanatmospheric pressure, arise. Upon a decrease in the internal pressure ofthe oil to a negative pressure level, air that is entrained in the oilduring the process of charging the bearing sections with oil, or that ispresent due to being swept in by the dynamic-pressure-generatinggrooves, appears in the form of bubbles. The volume of the bubblesexpands with increasing temperature or decreasing external environmentalpressure. The volume expansion of the bubbles brings leaking oil towardthe exterior of the bearing sections and impairs the spindle motor'sdurability and reliability. Furthermore, the dynamic-pressure-generatinggrooves that are formed in the bearing sections come into contact withthe bubbles, which causes vibrations and worsens non-repeatable run-out.The rotational precision of the spindle motor therefore worsens.Accordingly, the spindle motor configuration includes the communicatingpassage 110 in order to exhaust bubbles to the exterior of the bearingsections.

[0008] To bore the communicating passage 110 for discharging bubbles inthis way a drilling tool is used. The drill bit can only be so small,however, to be strong enough for machining, which limits how small thethrough-hole 110 a and the channels 110 b, 110 c that constitute thecommunicating passage 110 can be made. Consequently, the axial dimensionof the shaft 106 and the sleeve 102 must necessarily be at least a givensize for boring the communicating passage 110 and be extensive enough tomaintain bearing rigidity in the radial bearing sections 108, 108. Theserequirements stand in the way of making the spindle motor slimmer.

[0009] What is more, the fact that the through-hole 110 a as well as thechannels 110 b, 110 c that constitute the communicating passage 110 areformed in the sleeve 102 complicates that part of the structure and atthe same time increases the number of manufacturing processes. Anincreased-cost spindle motor is the result.

[0010] Further still, a ring element 112 that constitutes a retainer forthe rotor 100 is fitted onto the end portion of the shaft 106 on theside opposite the rotor 100. In short, because the thrust bearingsection 104; the radial bearing sections 108, 108; the through-hole 110a as well as the channels 110 b, 110 c that constitute the communicatingpassage 110; and the ring element 112 are arranged in the axialdirection stacked along the same axis, they create an impediment tomaking the spindle motor slimmer.

SUMMARY OF INVENTION

[0011] An object of the present invention is to simplify and slim downthe structure of a spindle motor while maintaining its rotationalstability.

[0012] Another object is in a spindle motor to maintain the internalpressure of the oil retained within the bearing gaps at or aboveatmospheric pressure, to enable preventing the occurrence of air bubbleswithin the oil.

[0013] Yet another object is balancing the internal pressure of the oilretained within the bearing gaps of a spindle motor.

[0014] A different object of the present invention is to enablepreventing particulate matter from being produced due to contact betweenthe rotor and stator components in a spindle motor.

[0015] Moreover, the present invention provides a low-profile, low-costdisk drive that can spin recording disks stably; and another object ofthe present invention accordingly is to enable preventing the occurrenceof read/write errors that originate in oil leaking out from, or inparticulate matter being produced by, the spindle motor in a disk drivedevice.

[0016] One example of a spindle motor under the present invention isconfigured with a radial dynamic-pressure bearing section, in betweenthe inner circumferential surface of the sleeve and the outercircumferential surface of the shaft, that induces hydrodynamic pressurein oil during rotation of the rotor. On at least either one of theupper-end face of the sleeve, or the bottom face of the rotor, the motoris also furnished with dynamic-pressure-generating grooves, configuringa thrust bearing section, that impart radially inward-heading pressureto the oil during rotation of the rotor. In addition, at its tip end theshaft is configured with an axial support section in which pressure thatessentially balances with the oil pressure within the thrust bearingsection is utilized.

[0017] Likewise, in another example of a spindle motor under the presentinvention, the shaft is formed unitarily with the rotor, wherein a roundtubular casing member whose outer peripheral surface functions as aradial bearing surface is attached to the outer peripheral surface ofthe shaft. A communicating pathway is formed in between the outercircumferential surface of the shaft and the inner circumferentialsurface of the casing member, enabling axial upper and lower ends of aradial bearing section formed in between the outer peripheral surface ofthe casing member and the inner peripheral surface of the sleeve tocommunicate.

[0018] Moreover, in a different example of a spindle motor under presentinvention, a thrust bearing is configured in between the upper-end faceof the sleeve, and the bottom-face of the hub, and a radial dynamicbearing is configured in between the inner circumferential surface ofthe sleeve and the outer circumferential surface of the shaft. Along itsouter circumferential surface the sleeve is furnished with a radiallyflaring annular flange portion, while on the inner circumferentialsurface of a round-cylindrical wall on the rotor, an annular memberwhose surface at least is harder than the sleeve is fixedly fitted. Theflange portion and the annular member engage with each other to form arotor retainer.

[0019] In one example of a disk drive under the present invention, thespindle motor that spins recording disks includes: a radialdynamic-pressure bearing section, in between the inner circumferentialsurface of the sleeve and the outer circumferential surface of theshaft, that induces hydrodynamic pressure in oil during rotation of therotor; and also a thrust bearing section provided withdynamic-pressure-generating grooves, on at least either one of theupper-end face of the sleeve or the bottom face of the rotor, thatimpart radially inward-heading pressure to the oil during rotation ofthe rotor. In addition, at its tip end the shaft has an axial supportsection in which pressure that essentially balances with the oilpressure within the thrust bearing section is utilized.

[0020] Likewise, in another example of a disk drive under the presentinvention, the shaft is formed unitarily with the rotor in thedisk-drive spindle motor for spinning recording disks, wherein a roundtubular casing member whose outer peripheral surface functions as aradial bearing surface is attached to the outer peripheral surface ofthe shaft. A communicating pathway is formed in between the outercircumferential surface of the shaft and the inner circumferentialsurface of the casing member, enabling axial upper and lower ends of aradial bearing section formed in between the outer peripheral surface ofthe casing member and the inner peripheral surface of the sleeve tocommunicate.

[0021] Moreover, in a different example of a disk drive under presentinvention, the spindle motor that spins recording disks includes: athrust bearing configured in between the upper-end face of the sleeve,and the bottom-face of the hub; and a radial dynamic bearing configuredin between the inner circumferential surface of the sleeve and the outercircumferential surface of the shaft. A radially flaring annular flangeportion is furnished on the outer circumferential surface of the sleeve,while on the inner circumferential surface of a rotor round-cylindricalwall, an annular member whose surface is at least harder than the sleeveis fixedly fitted. The flange portion and the annular member engage witheach other to form a rotor retainer.

BRIEF DESCRIPTION OF DRAWINGS

[0022]FIG. 1 is a sectional view that illustrates the configurationaloutline of a conventional spindle motor;

[0023]FIG. 2 is a sectional view that illustrates the configurationaloutline of a spindle motor in a first embodiment of the presentinvention;

[0024]FIG. 3 is a fragmentary enlarged sectional view that schematicallyillustrates the configuration of herringbone grooves formed in a radialbearing section of the spindle motor in the first embodiment of thepresent invention;

[0025]FIG. 4 is a plan view that schematically illustrates theconfiguration of spiral grooves formed in a thrust bearing section ofthe spindle motor in the first embodiment of the present invention;

[0026]FIG. 5 is a conceptual pressure-distribution diagram schematicallyillustrating pressure distribution in the spindle motor hydrodynamicbearing oil;

[0027]FIG. 6 is a sectional view that illustrates the configurationaloutline of a spindle motor in a second embodiment of the presentinvention;

[0028]FIG. 7 is an elevational, fragmentary view showing a portion ofthe shaft enlarged from the spindle motor depicted in FIG. 6;

[0029]FIGS. 8A through 8D are fragmentary enlarged sectional views thatschematically illustrate modified examples of the configuration ofherringbone grooves formed in a radial bearing section of the spindlemotor in a second embodiment of the present invention; and

[0030]FIG. 9 is a sectional view schematically illustrating the internalconfiguration of a disk drive.

DETAILED DESCRIPTION

[0031] First Embodiment

[0032] (1) Spindle Motor Configuration

[0033] Reference is made to FIG. 2, which illustrates a spindle motor ina first embodiment of the present invention. Set forth in FIG. 2, thespindle motor is furnished with: a rotor 6 made up of a rotor hub2—composed of an approximately disk-shaped top wall portion 2 a, and around-cylindrical peripheral wall portion 2 b depending downward fromthe outer rim of the top wall portion 2 a—and of a shaft 4 one endportion 4 a of which is perimetrically inserted into the central portionof the top wall portion 2 a of the rotor hub 2; a hollow, roundcylindrical sleeve 8 rotatively supporting the shaft 4; a sealing cap 10opposing the end face of the shaft 4 along its free end, and closingover the lower portion of the sleeve 8; and a bracket 12 formedintegrally with a round cylindrical portion 12 a for anchoring thesleeve 8.

[0034] The bracket 12 has a round cupped portion centered on the roundcylindrical portion 12 a; and a stator 14 having a plurality of teeththat project radially inward is arranged on the inner circumferentialsurface 12 b of a peripheral wall that the outer circumferential edge ofthe cupped portion defines. Likewise, a rotor magnet 16 that opposes thestator 14 via a radially inward clearance therefrom is fixedly fitted tothe outer circumferential surface of the peripheral wall portion 2 b ofthe rotor hub 2.

[0035] A flange-shaped disk-mounting portion 2 c for carrying recordingdisks on which information is recorded (in FIG. 6, represented asrecording disks 53) is formed on an outer circumferential portion of theperipheral wall portion 2 b of the rotor hub 2. A threaded hole 4 b isformed in the upper-end portion of the shaft 4 (its end at the top wallportion 2 a of the rotor hub 2). The recording disks are loaded onto thedisk-mounting portion 2 c, and after being retained by a clamp (notillustrated), the recording disks are fixedly secured to the rotor hub 2by fastening a screw (not illustrated) into the threaded hole 4 b.

[0036] An unbroken series of micro-gaps is formed in between theupper-end face of the sleeve 8 and the undersurface of the top wallportion 2 a of the rotor hub 2, and—continuing from the top wall portion2 a of the rotor hub 2—in between outer circumferential surface of theshaft 4 and the inner circumferential surface of the sleeve 8, andcontinuous therewith, in between the end face of the shaft 4 and theinner face of the sealing cap 10. Oil continuously fills the micro-gapswithout interruption, configuring a so-called full-fill hydrodynamicbearing structure. In this respect, the configuration of the bearingsand their supporting function will be described in detail later.

[0037] The upper-end portion of the sleeve 8 outer circumferentialsurface is made into an annular flange portion 8 a that flares radiallyoutward and that is contoured into an incline such that the outercircumferential surface contracts parting away from the upper-end faceof the sleeve 8. The flange portion 8 a radially opposes, without beingin contact with, the inner circumferential surface of the peripheralwall portion 2 b of the rotor hub 2.

[0038] Because as noted above the outer circumferential surface of theflange portion 8 a is contoured into an incline, the gap defined inbetween the inner circumferential surface of the peripheral wall portion2 b and the outer circumferential surface of the flange portion 8 aforms a taper whose radial clearance gradually increases heading axiallydownward (in the direction toward the distal rim of the peripheral wallportion 2 b). In particular, the inner circumferential surface of theperipheral wall portion 2 b and the outer circumferential surface of theflange portion 8 a cooperate to configure a taper-seal area 18. Withregard to the oil retained in the micro-gap series formed (as notedabove) in between the upper-end face of the sleeve 8 and theundersurface of the top wall portion 2 a of the rotor hub 2,and—continuing from the top wall portion 2 a of the rotor hub 2—inbetween outer circumferential surface of the shaft 4 and the innercircumferential surface of the sleeve 8, and continuous therewith, inbetween the end face of the shaft 4 and the inner face of the sealingcap 10: the oil-air boundary is in the taper-seal area 18 alone, andforms a meniscus where the oil surface tension and the outside airpressure balance.

[0039] The taper-seal area 18 functions as an oil reservoir, and inaccordance with the amount of oil retained within the taper-seal area18, the location where the boundary forms is movable to suit.Accordingly, attendant on reduction in the amount of oil retained, oilheld within the taper-seal area 18 is supplied to the bearing sections;and meanwhile, expanded oil due to thermal swelling is accommodatedwithin the taper-seal area 18.

[0040] In this way, the taper-shaped clearance is formed in between theouter circumferential surface of the flange portion 8 a of the sleeve 8,and the inner circumferential surface of the peripheral wall portion 2 bof the rotor hub 2, to configure the taper-seal area 18 employingsurface tension. This configuration makes the taper-seal area 18diametrically larger than the bearing sections, and meanwhile lets theaxial dimension of the taper-seal area 18 be relatively large.Consequently, the volumetric capacity within the taper-seal area 18 isenlarged, making it sufficiently complementary for thermal expansion ofthe greater amount of oil retained in hydrodynamic bearings having thefull-fill structure.

[0041] An annular retaining ring 20 is fixedly attached by means of anadhesive to the peripheral wall portion 2 b at its end distally beyondthe taper-seal area 18. The retaining ring 20 fits into place at thelower-end portion of the outer circumferential surface of the sleeve 8without coming into contact against the lower part of the flange portion8 a, whereby a structure that keeps the rotor 6 from coming out from thesleeve 8 is configured. By thus configuring the rotor 6 retainingstructure along the outer circumferential surface of the sleeve 8, apair of radial bearings, which will later be described in detail, andthe retaining structure are not arranged lying in a row along the sameaxis. This accordingly enables the entire length of the shaft 4 to beput to effective use as a bearing, and makes it possible to scale downthe motor into a lower profile while maintaining bearing rigidity.

[0042] Here, arranging the rotor 6 retaining structure external to thebearings, as is the case with the spindle motor illustrated in FIG. 2,in order to slim the profile of the motor means that the retainer isdisposed within the air (referred to hereinafter as “the dry area”).

[0043] In a hard disk drive, for example, in order to shorten seek timethe heads and the recording surface of the recording disks are separatedby a clearance of as little as 1 μm or less. Therefore, evenmicro-particles can get caught in the clearance between a head and arecording surface, becoming the causative source of a so-called headcrash. For spindle motors employed under such environments, this sort ofparticle spatter is a serious problem in terms of quality.

[0044] If the retainer were to be configured inside the bearings, metalabrasion dust that would be produced during rotation by contactoccurring in the retainer section due to exteriorly acting vibrationsand shock would be captured by the oil retained in the bearing sections.The dust therefore could not be scattered away to the spindle motorexterior. In contrast, configuring the retainer section in the dry areameans that particulate matter produced in the retainer section readilygets scattered away to the exterior of the spindle motor.

[0045] The production of particulate matter during contact becomes evenmore pronounced in those particular situations in which the rotary-sidecomponents and the stationary-side components that compose the retainingsection are made from the same type of metal.

[0046] Under these circumstances, making the retaining ring 20 harder atleast on its surface than the sleeve 8 makes scaling down the motorprofile while gaining desired rotational precision a reality. At thesame time, the at least superficially harder retaining ring 20 enablespreventing as much as possible the production of particulate matter dueto contact between the retaining ring 20 and the sleeve 8 that togetherconstitute the retainer. Accordingly, even if exterior vibrations andshock have an impact on the spindle motor when the rotor 6 spins, andcontact between the retaining ring 20 and the sleeve 8 occurs, thegeneration of particulate matter will be prevented.

[0047] In this instance, forming the retaining ring 20 from a ceramicmaterial makes surer prevention of the production of particulate matterpossible, without increasing the manufacturing process steps.

[0048] Likewise, generation of particulate matter due to contact betweenthe sleeve 8 and the retaining ring 20 can be prevented by forming theretaining ring 20 from, e.g., a stainless-steel material and carryingout a surface-hardening process on the surface thereof. Nickel plating,DLC (diamond-like carbon) coating, or nitriding treatments arepreferable as surface treatments in this case.

[0049] As far as forming the retaining section is concerned, in eitherof the foregoing cases, the sleeve 8 and retaining ring 20 can be madefrom raw materials that differ—formed using a stainless-steel materialor a copper raw material.

[0050] The upper face of the retaining ring 20 opposes the undersurfaceof the flange portion 8 a across an axial gap that is continuous withthe taper-seal area 18 and whose clearance is smaller than the minimumclearance of the radial gap in the taper-seal area 18.

[0051] By establishing the clearance of the axial micro-gap definedbetween the upper face of the retaining ring 20 and the undersurface ofthe flange portion 8 a to be as small as possible, it functions as alabyrinth seal when the spindle motor is spinning. The differencebetween the air current speed in the axial micro-gap and the air currentspeed in the radial clearance defined in the taper-seal area 18 is thusenlarged, and the resistance to outflow of oil vapor occurring due togasification is made greater. This keeps the vapor pressure in thevicinity of the oil boundary surface high, so as further to preventvapor dispersal of the oil.

[0052] Setting up a labyrinth seal in this way in association with thetaper-seal area 18 not only checks outflow of oil as a fluid, but makesit possible to deter outflow to the motor exterior of oil mist producedby the oil gasifying due to elevation in the exterior ambienttemperature of the motor. This consequently works to prevent decline inthe retained amount of oil and maintain stabilized bearing performanceover the long term, making the bearings highly durable and reliable.

[0053] (2) Bearing Configuration

[0054] Herringbone grooves 22 a as illustrated in FIG. 3 are formed onthe inner circumferential surface of the sleeve 8 by its upper-end faceso as to induce hydrodynamic pressure in the oil when the rotor 6 spins.Each of the herringbone grooves 22 a is configured by a pair of linkedspiral grooves 22 a 1 and 22 a 2 inclining into each other from mutuallyopposing directions with respect to the rotary direction. An upperradial hydrodynamic bearing section 22 is constituted between the innercircumferential surface of the sleeve 8 where the grooves 22 a areformed and the outer circumferential surface of the shaft 4.

[0055] Likewise, herringbone grooves 24 a are formed on the innercircumferential surface of the sleeve 8 by the free-end portion of theshaft 4 so as to induce hydrodynamic pressure in the oil when the rotor6 spins. Each of the herringbone grooves 24 a is configured by a pair ofspiral grooves 24 a 1 and 24 a 2 inclining into each other from mutuallyopposing directions with respect to the rotary direction. A lower radialhydrodynamic bearing section 24 is constituted between the innercircumferential surface of the sleeve 8 where the grooves 24 a areformed and the outer circumferential surface of the shaft 4.

[0056] Here, the herringbone grooves 22 a, 24 a that are formed in theupper and lower radial hydrodynamic bearing sections 22, 24 areestablished so that the spiral grooves 22 a 1 and 22 a 2, and 24 a 1 and24 a 2 generate essentially equal pumping force—so that the groovefundamentals, which are axial dimension, inclination angle with respectto the rotary direction, or groove width and depth, will be the same.That is, the herringbone grooves 22 a, 24 a are established so as to beaxially symmetrical with respect to where the spiral grooves 22 a 1 and22 a 2, and 24 a 1 and 24 a 2 join. Accordingly, in the upper and lowerradial hydrodynamic bearing sections 22, 24 maximum pressure appears inthe axially central portion (where the spiral grooves join) of eachbearing section, meaning that the pumping action by the spiral grooves22 a 1 and 22 a 2, and 24 a 1 and 24 a 2 is non-uniform with respect toeither direction axially, whereby no axial flow is generated in the oil.

[0057] In addition, as illustrated in FIG. 4 pump-in spiral grooves 26 aare formed on the upper-end face of the sleeve 8 so as to induceradially inward-heading pressure (toward the shaft 4) in the oil whenthe rotor 6 spins, and a thrust bearing section 26 is constitutedbetween the upper-end face of the sleeve 8 and the undersurface of therotor hub 2 top wall portion 2 a.

[0058] Accordingly, structuring the spindle motor to be a full-fill typebearing configuration while maintaining desired bearing rigidity and—innot requiring a thrust plate to configure the thrust hydrodynamicbearing—retaining a simplified, reduced-cost enabling structure makes itpossible further to slim the motor profile and lower its cost.

[0059] Likewise, an axial support section 28 that, as will later bedescribed in detail, employs oil internal pressure heightened by thespiral grooves 26 a of the thrust bearing section 26, is configured inbetween the free-end end face of the shaft 4 and the inner face of thesealing cap 10 as a hydrostatic bearing section.

[0060] (3) Manner in Which Rotor is Supported

[0061] How the rotor 6 is supported by the bearings configured asdescribed in the foregoing will be detailed with reference to FIG. 5.Here, FIG. 5 is a pressure-distribution chart schematically representingrelative relationships in pressure distribution, developing from bearingto bearing, of the oil retained in the micro-gap formed in between theupper-end face of the sleeve 8 and the undersurface of the top wallportion 2 a of the rotor hub 2, and—continuing from the top wall portion2 a of the rotor hub 2—in between outer circumferential surface of theshaft 4 and the inner circumferential surface of the sleeve 8, andcontinuous therewith, in between the end face of the shaft 4 and theinner face of the sealing cap 10. Because the pressure distribution inthe spindle motor is axially symmetrical, however, the pressuredistribution with respect to the rotational center axis, indicated bythe dotted-dashed line in FIG. 5, for the region that would be on theopposite side of a vertical section through the spindle motor isomitted. Further, the numbers shown in FIG. 5 are the same numbers thatmark each of the bearing sections in FIG. 2.

[0062] Accompanying rotation of the rotor 6, the pumping force from theherringbone grooves 22 a, 24 a in the upper and lower radialhydrodynamic bearings 22, 24 is heightened, producing hydrodynamic fluidpressure. As indicated by the distribution graph in FIG. 5, the pressurethrough the herringbone grooves 22 a, 24 a in the upper and lower radialhydrodynamic bearings 22, 24 rises abruptly at their either ends,becoming maximal in the places where the spiral grooves 22 a 1 and 22 a2, and 24 a 1 and 24 a 2 join. Utilizing the hydrodynamic pressuregenerated in the upper and lower radial hydrodynamic bearings 22, 24,the shaft 4 is supported axially along its upper/lower ends, and actionsthat center the shaft 4 and restore it from deviations are borne.

[0063] Accompanying rotation of the rotor 6, radially inward-headingpressure is induced in the oil in the thrust bearing section 26 by thepump-in spiral grooves 26 a. The flow of the oil is accelerated by theradially inward-heading pressure, raising the oil internal pressure andgenerating hydrodynamic pressure acting in a lifting direction on therotor 6. As indicated in FIG. 5, the hydrodynamic pressure induced inthe thrust bearing section 26 does not rise abruptly as is the case withthe upper and lower radial hydrodynamic bearings 22, 24; rather, atmaximum it is at a level exceeding atmospheric pressure to a certaindegree.

[0064] Owing to the pressure generated in the thrust bearing section 26,pressure-wise the oil retained—continuing from the top wall portion 2 aof the rotor hub 2—in between outer circumferential surface of the shaft4 and the inner circumferential surface of the sleeve 8, and continuoustherewith, in between the end face of the shaft 4 and the inner face ofthe sealing cap 10 is essentially sealed. Likewise, the fact that theherringbone grooves 22 a, 24 a formed in the upper and lower radialhydrodynamic bearings 22, 24 have an axially symmetrical form, and thatthe dynamic pressure generated is balanced in the axial direction meansthat, as described above, axially directed flow is not induced in theoil. Thus, the internal pressure of the oil retained in between theouter circumferential surface of the shaft 4 and the innercircumferential surface of the sleeve 8, and continuous therewith, inbetween the end face of the shaft 4 and the inner face of the sealingcap 10 balances with the internal pressure of the oil retained in thethrust bearing section 26. Accordingly, as indicated in FIG. 5, ineither of these areas the internal pressure of the oil will be on parwith that of the oil retained in the thrust bearing 26. Negativepressure, wherein the internal pressure would go below atmosphericpressure, will not be generated in the oil retained within thesemicro-gaps.

[0065] Problems with leakage of oil out to the bearing exterior, withvibrations, or with worsening of non-repeatable run-out, which arise dueto air bubbles residing within the oil, are accordingly prevented fromoccurring. Thus, a communicating passage for communicating the bearinginterior with the external air is thereby rendered unnecessary.

[0066] As noted above, the pressure generated in the thrust bearing 26it is at a level exceeding atmospheric pressure to a certain degree, butthis pressure alone is unlikely to lift the rotor 6 sufficiently.Nevertheless, the internal pressure of the oil retained in the axialsupport section 28 formed between the free-end end face of the shaft 4and the inner face of the sealing cap 10 as described above will bepressure equal to the oil internal pressure heightened by thehydrodynamic pressure induced in the thrust bearing section 26. That is,although a hydrodynamic bearing is not configured between the inner faceof the sealing cap 10 and the end face of the shaft 4, the axial supportsection 28—which functions as a so-called hydrostatic pressure bearing,and which in cooperation with the thrust bearing 26 allows the rotor 6to be lifted—is configured.

[0067] Accordingly, the thrust bearing section 26 and the axial support(hydrostatic bearing) section 28 cooperate to enable the rotor 6 to besufficiently lifted.

[0068] Here, as illustrated in FIG. 2 an annular thrust yoke 30 made ofa ferromagnetic material is disposed in a position on the bracket 12opposing the rotor magnet 16. This generates axially directed magneticattraction between the rotor magnet 16 and the thrust yoke 30 thatbalances the lifting pressure on the rotor 6 generated in the thrustbearing section 26 and the axial support section 28, stabilizes thethrust-directed support of the rotor 6, and controls occurrence ofover-lift that would buoy the rotor 6 more than necessary. A thusmagnetically urging force can also be made to act on the rotor 6 by, forexample, displacing the magnetic centers of the stator 14 and the rotormagnet 16 in the axial direction.

[0069] Second Embodiment

[0070] (4) Spindle Motor Configuration

[0071] Next, using FIGS. 6 through 8 the configuration of a spindlemotor in a second embodiment of the present invention will be described.Here, components in the second embodiment that are identical with thefirst embodiment are marked with the same reference numerals, andexplanation thereof is omitted. Likewise, the bearing configuration isessentially identical with the first embodiment, as is the way in whichthe bearings support the rotor, and the configuration is thereforemarked with the same reference numerals.

[0072] Set forth in FIG. 6, the spindle motor includes: a rotor 6# madeup of a rotor hub 2#—composed of an approximately disk-shaped top wallportion 2#a, and a round-cylindrical peripheral wall portion 2 bdepending downward from the outer rim of the top wall portion 2 a—and ofa shaft 4# formed integrally with the central part of the top wallportion 2#a of the rotor hub 2#; and a round-cylindrical casing member 5that is fitted to the outer circumferential surface of the shaft 4#.

[0073] (5) Configuration and Function of Communicating Pathway

[0074] Reference is made now to FIG. 7, which is an elevational viewrepresenting the shaft 4# enlarged. As illustrated in FIG. 7, a singlehelical groove 4 a# (represented in part by dashed lines) is furnishedon the outer circumferential surface of the shaft 4#, running in theaxial direction from its upper to its lower end.

[0075] The helical groove 4 a# is formed by a machining process to havea sectional contour that is approximately rectangular or triangular, orelse semicircular. Here, when carrying out the process of machining thehelical groove 4#a into the outer circumferential surface of the shaft4#, the process can be carried out in a single chucking.

[0076] With the casing member 5 fitted onto the outer circumferentialsurface of the shaft 4#, in between it and the inner circumferentialsurface of the casing member 5# a helix-shaped communicating pathway 7is defined by the helical groove 4#a. The communicating pathway 7 runsalong the inner circumferential surface of the casing member 5# from theupper to the lower end portion in the axial direction, i.e., the pathway7 is continuous with the micro-gaps formed in thrust bearing section 26and the axial support section 28. Within the communicating pathway 7,oil is retained continuously with the oil held in the thrust bearingsection 26 and in the axial support section 28. Likewise, the internalpressure of the oil retained within the communicating pathway 7 balanceswith the internal pressure of the oil retained in the bearing sections.

[0077] It can sometimes happen that on account of manufacturingdiscrepancies in the inner circumferential surface of the sleeve 8 andthe outer circumferential surface of the casing member 5 becomingcombined in the worst case scenario within tolerances, or due to theimpact of stresses that occur in fastening the screw into the threadedhole 4#b provided in the shaft for retaining recording disks on the diskdisk-mounting portion 2#c of the rotor hub 2#, the clearance of themicro-gap formed in between the inner circumferential surface of thesleeve 8 and the outer circumferential surface of the casing member 5will be non-uniform between the upper-end and lower-end sides in theaxial direction. Should the micro-gap formed between the sleeve 8 innercircumferential surface and the casing member 5 outer circumferentialsurface be non-uniform, an abnormal flow will be induced in the oil. Asa consequence, a disparity in internal pressure of the oil in the upperend and in the lower end axially of the micro-gap formed between thesleeve 8 inner circumferential surface and the casing member 5 outercircumferential surface—i.e., a pressure disparity between the thrustbearing section 26 and the axial support section 28—will arise. If thisoil internal pressure difference is left as is, oil will happen to flowfrom the lower to the upper end axially, giving rise to negativepressure in the axial support section 28. Likewise, oil will happen toflow from the upper to the lower end axially, raising the internalpressure of the oil in the axial support section 28 more than isnecessary and producing over-lift on the rotor 6.

[0078] Countering this, the communicating pathway 7 that is continuouswith micro-gaps formed in the thrust bearing section 26 and the axialsupport section 28, and that retains oil continuously with the oilretained in these thrust-bearing and bearing sections 26 and 28, isprovided. Therefore, even if the above-noted axial flow is induced inthe oil, and a disparity arises in the internal pressure of the oil inthe upper end and in the lower end axially of the micro-gap formedbetween the sleeve 8 inner circumferential surface and the casing member5 outer circumferential surface, because a flow of oil passing throughthe communicating pathway 7 from the internal-pressure high end to thelow end will occur, the internal pressure of the oil retained in each ofthe bearing areas will balance, preventing incidents of negativepressure and over-lift.

[0079] The presence of a communicating pathway 7 as in the foregoing ina spindle motor of the second embodiment means that in the herringbonegrooves 22 a and 24 a in the radial bearing sections 22 and 24 formed inbetween the inner circumferential surface of the sleeve 8 and the outercircumferential surface of the casing member 5, configurations such asindicated in FIGS. 8A through 8D for the spiral grooves 22 a 1 and 22 a2, and 24 a 1 and 24 a 2 that form the herringbone grooves 22 a and 24a, other than being symmetrical with respect to where they join—as isthe case in the first embodiment—are possible.

[0080] (6) Modified Examples of Second Embodiment

[0081] (6-1) Modification Example 1

[0082] In the modification example diagrammed in FIG. 8A herringbonegrooves 22 a# formed in an upper radial bearing section 22# have anasymmetrical configuration in the axial direction, while the herringbonegrooves 24 a formed in the lower radial bearing section 24 have asymmetrical configuration with respect to where they join, likewise asis the case in the first embodiment.

[0083] To be more specific: In the herringbone grooves 22 a# formed inthe upper radial bearing section 22#, spiral grooves 22 a#1 locatedtoward the upper end of the sleeve 8 (thrust bearing section 26) areestablished so as to be longer in axial dimension than spiral grooves 22a#2 located toward the lower radial bearing section 24. Consequently,the place in which the pairs of spiral grooves 22 a#1 and 22 a#2 join islower than the center of the upper radial bearing section 22#—i.e., islocated biased toward the lower radial bearing section 24. Therefore,the pumping action by the spiral grooves 22 a#1 on the oil when therotor 6 spins surpasses the pumping action by the spiral grooves 22 a#2,which in terms of the upper radial bearing section 22# induces in theoil a flow heading toward the lower end of the sleeve 8 (toward thelower radial bearing section 24).

[0084] Rendering the herringbone grooves 22 a# in the upper radialbearing section 22# in an axially unbalanced configuration in this waykeeps the pressure in the region between the upper radial bearingsection 22# and the lower radial bearing section 24 at positive pressuregreater than atmospheric, preventing the occurrence of negativepressure. Then on account of the pressuring force generated in theherringbone grooves 22 a# the oil always flows toward the lower end ofthe sleeve 8; and oil that has flowed toward the lower end of the sleeve8 recirculates through the communicating pathway 7 from along the lowerend to along the upper end of the sleeve 8, and is pushed in toward thelower end of the sleeve 8 all over again by the upper radial bearingsection 22#, wherein a constant oil circulation path is formed.

[0085] Thus the herringbone grooves 22 a# causing the oil to flow at alltimes in a predetermined direction within the bearing gaps provides forstability in the balance of pressure in every region in the oil retainedwithin the bearing gaps, which ensures that occurrences of negativepressure and of over-lift on the rotor 6 are prevented. What is more,even in instances where manufacturing discrepancies or deformationstress during assembly have occurred, with oil circulation in a constantdirection being secured the acceptable range—beyond which isunacceptability whose fault lies in processes and assembly—is markedlyenlarged, therefore bettering yields.

[0086] (6-2) Modification Example 2

[0087] Then as diagrammed in FIG. 8B, it is also possible to render inan axially asymmetrical configuration not only the upper radial bearingsection 22#, but also the lower radial bearing section 24#, in a makeupwhere among the spiral grooves 24 a#1 and 24 a#2constituting theherringbone grooves 24 a# formed therein, establishing the spiralgrooves 24 a#1, located toward the upper radial bearing section 22#, soas to be longer in axial dimension than the spiral grooves 24 a#2,located toward the lower end of the sleeve 8, positions the place inwhich they join biased toward the lower end of the sleeve 8.

[0088] Thus configuring not only the upper radial bearing section 22#but also the lower radial bearing section 24# so as induce in the oil aflow heading toward the lower end of the sleeve 8 makes the pressure inthe hydrostatic bearing section 28 higher, and strengthens the liftingforce on the rotor 6. Because this accordingly makes it so thathigher-burden loads can be supported, utilization in situations where aplurality of disks is rotationally driven is made possible. Furthermore,a more active circulation is urged upon the oil, which is effective inpreventing occurrences of negative pressure and of over-lift on therotor 6.

[0089] (6-3) Modification Example 3

[0090] With modification example 3, diagrammed in FIG. 8C, in theherringbone grooves 22 a# formed in the upper radial bearing section 22#the spiral grooves 22 a#1 located toward the thrust bearing section 26are established so as to be longer in axial dimension than the spiralgrooves 22 a#2 located toward the lower radial bearing section 24,likewise as is the case in modification examples 1 and 2, so that a flowtoward the lower radial bearing section is generated in the oil. What isdifferent, however, is that in herringbone grooves 24 a# formed in lowerradial bearing section 24#, spiral grooves 24 a#2 located toward thelower end of the sleeve 8 are formed so as to be slightly longer inaxial dimension than spiral grooves 24 a#1 located toward the upperradial bearing section 22#.

[0091] This configuration consequently prompts an oil flow heading fromalong the lower radial bearing section 24# toward the upper radialbearing section 22#, preventing incidence of negative pressure in theregions between the upper radial bearing section 22# and the lowerradial bearing section 24#. It should be understood that as thedimensional difference between the spiral grooves 24 a#1 and the spiralgrooves 24 a#2 making up the herringbone grooves 24 a# of the lowerradial bearing section 24# is less than the dimensional difference inthe herringbone grooves 22 a# of the upper radial bearing section 22#,oil flow generated in the upper radial bearing section 22# and headingtoward the lower radial bearing section 24# is therefore not hindered bythe oil flow that the lower radial bearing section 24# generates headingtoward the upper radial bearing section 22#.

[0092] (6-4) Modification Example 4

[0093] An additionally possible modification, as diagrammed in FIG. 8D,is to render the herringbone grooves in the upper radial bearing sectionherringbone grooves 22 a likewise as in the first embodiment, in aconfiguration symmetrical with respect to the joints, and to render theherringbone grooves in the lower radial bearing section herringbonegrooves 24 a# likewise as with Modification Example 2 illustrated inFIG. 8B, in an asymmetrical form biased toward the lower end of thesleeve 8. In this case, the dimensional difference between the spiralgrooves 24 a#1 and 24 a#2 in the lower radial bearing section 24# isless than is the case with the herringbone grooves on the upper radialbearing section side rendered in an asymmetrical configuration.Consequently, a relatively large bearing span between upper and lowerradial bearing sections 22 and 24# can be secured to make it possible toenhance bearing rigidity, while an oil flow heading toward the lower endof the sleeve 8 is still generated to expand tolerance in terms ofmanufacturing discrepancy or deformation stress during assembly.

[0094] Here, inducing in the oil a flow heading from along the radialbearing sections toward the lower end of the sleeve 8, as indicated inFIGS. 8A through 8D, means that the internal pressure of the oilretained in the hydrostatic bearing section 28 balances to the sum offlow pressure induced in the thrust bearing section 26 and the flowpressure of the oil from along the radial bearing sections. This enablesmore stabilized support with increased bearing load capacity.

[0095] (7) Configuration of Disk Drive Device

[0096] Reference is made to FIG. 9, in which the internal configurationof a disk drive 50 is illustrated as an exemplary diagram. A clean spacewhere dust and debris are extremely slight is formed inside a housing51, in the interior of which is disposed a spindle motor 52 on whichplatter-shaped recording disks for data recordation are fitted. Inaddition, a head-shifting mechanism 57 that reads data from and writesdata onto the recording disks 53 is disposed within the housing 51. Thehead-shifting mechanism 57 is composed of heads 56 that read/write dataon the recording disks 53; arms 55 that support the heads 56; and anactuator 54 that shifts the heads 56 and arms 55 over the neededlocations on the recording disks 53.

[0097] Employing a spindle motor under the first or second embodimentsof the present invention as the spindle motor 52 for the disk drive 50as such yields desired rotational precision while making it possible toscale the disk drive 50 down into a lower profile and reduce its cost.In addition, the reliability and durability of the disk drive 50 may beimproved.

[0098] While spindle-motor and disk-drive embodiments in accordance withthe present invention have been explained in the foregoing, the presentinvention is not limited to these embodiments. Various changes andmodifications are possible without departing from the scope of theinvention.

[0099] For example, instead of the pump-in type of spiral grooves 26 athat were described in the foregoing embodiments, herringbone groovesthat in the radial direction are asymmetrical in contour would bepossible as the means provided in the thrust bearing section forgenerating pressure that acts radially inward on the oil. This wouldestablish a situation in which pumping force from the spiral, radiallyoutwardly located grooves would exceed pumping force from the spiral,radially inwardly located grooves. The amount of imbalance in pumpingforce between the spiral groove areas would therefore be pressure actingradially inward on the oil.

[0100] Here, in a situation in which the above-described herringbonegrooves are furnished in the thrust bearing section, the lifting forceimparted to the rotor will be higher than the lifting force generated inthe spiral grooves. The load-supporting force from the thrust bearingsection therefore will be improved, but a downside tied in with thelifting force being generated in the bearing sections is a concern thatover-lift on the rotor will arise. Consequently, this must be controlledby means of magnetic urging force imparted to the rotor.

What is claimed is:
 1. A spindle motor, comprising: a shaft; a sleeveformed with a through-hole for rotary-play insertion of the shaft; arotor having a round top plate in the rotational center of which theshaft is constituted integrally, and a circular cylindrical walldepending from the top plate along its outer rim; a cover member forclosing over one end of the through-hole formed in the sleeve;micro-gaps formed continuing between an upper-end face of said sleeveand a bottom face of said rotor top plate, an inner circumferentialsurface of said sleeve and an outer circumferential surface of saidshaft, and an inner face of said cover member and an end face of saidshaft; oil retained continuously without interruption within saidmicro-gaps throughout their entirety; a radial dynamic pressure bearingsection configured between said sleeve inner-circumferential surface andsaid shaft outer-circumferential surface, for inducing hydrodynamicpressure into said oil when said rotor spins; a thrust bearing sectionconfigured on at least one of either said sleeve upper-end face or saidtop plate bottom face, and furnished with dynamic-pressure-generatingstriations for imparting to said oil radially inward-heading pressurewhen said rotor spins; herringbone grooves being contiguous pairs ofspiral grooves for generating essentially equal pressure, provided asdynamic-pressure-generating striations in said radial dynamic-pressurebearing section; and an axial support section, formed between said covermember inner face and said shaft end face, having pressure essentiallybalancing radially inward-heading pressure generated in said thrustbearing section, wherein said rotor is lifted through cooperation ofsaid thrust bearing section and said bearing section.
 2. A spindle motoras set forth in claim 1: an outer circumferential surface of said sleeveand an inner circumferential surface of said rotor circular cylindricalwall opposing via a radial gap; and said sleeve along its outercircumferential surface being provided with a taper surface constrictingin outer diameter according as its separation from said rotor top plate;wherein said oil is retained by a meniscus forming in between said tapersurface and the inner-circumferential surface of said rotor circularcylindrical wall.
 3. A spindle motor as set forth in claim 2, wherein: astepped portion continuous with said taper surface is provided in saidsleeve by recessing its outer circumferential surface radially inwardly;an annular member projecting radially inward corresponding to thestepped portion is fixedly fitted into the inner circumferential surfaceof said rotor circular cylindrical wall, and a rotor retainer isconstituted by engagement of the stepped portion and the annular member;a micro-gap, smaller than the minimum clearance of the radial gap formedbetween the taper surface of said sleeve and the inner circumferentialsurface of said rotor circular cylindrical wall, is formed to functionas a labyrinth seal between said annular member along its upper face andsaid sleeve stepped portion along its undersurface.
 4. A spindle motoras set forth in claim 1, wherein said radial dynamic-pressure bearingsection is configured between said shaft outer-circumferential surfaceand said sleeve inner-circumferential surface as an axially separatedpair of radial dynamic-pressure bearings.
 5. A spindle motor as setforth in claim 1, wherein said rotor is urged in a direction toward saidcover member by axially acting magnetic force.
 6. A spindle motorcomprising: a shaft; a sleeve formed with a through-hole for rotary-playinsertion of the shaft; a rotor having a round top plate in therotational center of which the shaft is furnished united, and a circularcylindrical wall depending from the top plate along its outer rim; acover member for closing over one end of the through-hole formed in thesleeve; a circular cylindrical casing member fitted to said shaft overits outer circumferential surface micro-gaps formed continuing betweenan upper-end face of said sleeve and a bottom face of said rotor topplate, an inner circumferential surface of said sleeve and an outercircumferential surface of said casing member, and an inner face of saidcover member and end faces of said shaft and said casing member; oilretained continuously without interruption within said micro-gapsthroughout their entirety; a radial dynamic-pressure bearing sectionconfigured intermediarily by at least one surface of either said sleeveinner-circumferential surface or said casing memberouter-circumferential surface, and by said oil when said rotor spins,and provided with, as dynamic-pressure-generating striations,herringbone grooves for inducing into said oil when said rotor spinshydrodynamic pressure; a thrust bearing section configured on at leastone of either said sleeve upper-end face or said top plate bottom face,and furnished with dynamic-pressure-generating striations for impartingto said oil radially inward-heading pressure when said rotor spins; anaxial support section, formed between said cover member inner face andsaid shaft end face, having pressure essentially balancing radiallyinward-heading pressure generated in said thrust bearing section,wherein said rotor is lifted through cooperation of said thrust bearingsection and said bearing section; and a communicating pathway formed inbetween said shaft along its outer circumferential surface and saidcasing member along its inner circumferential surface, for communicatingsaid oil retained in, and enabling it to circulate between, themicro-gap formed between said sleeve upper-end face and the bottom faceof said rotor top plate, and the micro-gap formed between said covermember inner face and said shaft and casing member end faces.
 7. Aspindle motor as set forth in claim 6: a helical groove being formed onthe outer circumferential surface of said shaft in a single path runningfrom its upper-end portion to its lower-end portion; wherein fittingsaid casing member over the outer circumferential surface of said shaftdefines said communicating pathway between said helical groove and theinner circumferential surface of said casing member.
 8. A spindle motoras set forth in claim 6: an outer circumferential surface of said sleeveand an inner circumferential surface of said rotor circular cylindricalwall opposing via a radial gap; and said sleeve outer circumferentialsurface being provided with a taper surface constricting in outerdiameter according as its separation from said rotor top plate; whereinand said oil is retained by a meniscus forming in between said tapersurface and the inner-circumferential surface of said rotor circularcylindrical wall.
 9. A spindle motor as set forth in claim 8, wherein: astepped portion continuous with said taper surface is provided in saidsleeve by recessing its outer circumferential surface radially inwardly;an annular member projecting radially inward corresponding to thestepped portion is fixedly fitted into the inner-circumferential surfaceof said rotor circular cylindrical wall, and a rotor retainer isconstituted by engagement of the stepped portion and the annular member;a micro-gap smaller than the minimum clearance of the radial gap formedbetween the taper surface of said sleeve and the inner-circumferentialsurface of said rotor circular cylindrical wall, is formed to functionas a labyrinth seal between the annular member along its upper face andsaid sleeve stepped portion along its undersurface.
 10. A spindle motoras set forth in claim 6, said radial dynamic-pressure bearing sectionbeing configured between said shaft outer-circumferential surface andsaid sleeve inner-circumferential surface as an axially separated pairof radial dynamic-pressure bearing constituents, wherein as thedynamic-pressure-generating striations in each radial bearingconstituent, herringbone-groove forming contiguous pairs of spiralgrooves for inducing into said oil when said rotor spins hydrodynamicpressure whose pressure gradient becomes axially symmetrical areprovided.
 11. A spindle motor as set forth in claim 6, said radialdynamic-pressure bearing section being configured between said shaftouter-circumferential surface and said sleeve inner-circumferentialsurface as an axially separated pair of radial dynamic-pressure bearingconstituents, wherein as the dynamic-pressure-generating striations inat least one of either said pair of radial dynamic-pressure bearingconstituents, asymmetrically configured herringbone grooves for inducinginto said oil when said rotor spins hydrodynamic pressure actingunidirectionally in the axial direction are provided.
 12. A spindlemotor as set forth in claim 6, wherein said rotor is urged in adirection toward said cover member by axially acting magnetic force. 13.A spindle motor, comprising: a shaft; a sleeve formed with athrough-hole for rotary-play insertion of the shaft; a rotor having around top plate in the rotational center of which the shaft isconstituted integrally, and a circular cylindrical wall depending fromthe top plate along its outer rim; a thrust bearing section configuredon at least one of either said sleeve upper-end face or said top platebottom face, and furnished with dynamic-pressure-generating striationsfor imparting to said oil radially inward-heading pressure when saidrotor spins; a radial dynamic pressure bearing section configuredbetween said sleeve inner-circumferential surface and said shaftouter-circumferential surface, for inducing hydrodynamic pressure intosaid oil when said rotor spins; an annular flange portion with whichsaid sleeve is provided wherein its outer circumferential surface flaresradially outward, and an annular member, projecting radially inward in alocation corresponding to said flange portion along its underside,fixedly fitted into an inner circumferential surface of said rotorcircular cylindrical wall, a rotor retainer being constituted byengagement of the flange portion and the annular member; wherein saidannular member is harder at least superficially than said sleeve.
 14. Aspindle motor as set forth in claim 13, wherein said annular member isformed from a ceramic material.
 15. A spindle motor as set forth inclaim 13, wherein said annular member is formed from a surface-hardenedmetal material.
 16. A spindle motor as set forth in claim 13, wherein:one end of the through-hole formed in the sleeve is closed over by acover member; micro-gaps are formed continuing between an upper-end faceof said sleeve and a bottom face of said rotor top plate, an innercircumferential surface of said sleeve and an outer circumferentialsurface of said shaft, and an inner face of said cover member and an endface of said shaft, meanwhile oil is retained continuously withoutinterruption within said micro-gaps throughout their entirety; andherringbone grooves being contiguous pairs of spiral grooves forgenerating essentially equal pressure are provided asdynamic-pressure-generating striations in said radial dynamic-pressurebearing section, an axial support section is formed between said covermember inner face and said shaft end face, having pressure essentiallybalancing radially inward-heading pressure generated in said thrustbearing section, wherein said rotor is lifted through cooperation ofsaid thrust bearing section and said bearing section, meanwhile saidrotor is magnetically urged in a direction axially opposing its liftingdirection.
 17. A spindle motor as set forth in claim 16: said flangeportion along its outer circumferential surface and said rotor circularcylindrical wall along its inner circumferential surface opposing via aradial gap; and said flange portion along its outer circumferentialsurface being provided with a taper surface constricting in outerdiameter according as its separation from said rotor top plate; whereinsaid oil is retained by a meniscus forming in between said taper surfaceand the inner-circumferential surface of said rotor circular cylindricalwall, meanwhile a micro-gap, smaller than the minimum clearance of theradial gap formed between the taper surface along said flange portionouter circumferential surface and the inner circumferential surface ofsaid rotor circular cylindrical wall, is formed to function as alabyrinth seal between said annular member along its upper face and saidflange portion along its undersurface.
 18. A disk-drive device includinga housing, a spindle motor fixed inside said housing for spinningrecording disks, and an information access means for writing informationinto and reading information out from needed locations on the recordingdisks, wherein said spindle motor comprises: a shaft; a sleeve formedwith a through-hole for rotary-play insertion of the shaft; a rotorhaving a round top plate in the rotational center of which the shaft isconstituted integrally, and a circular cylindrical wall depending fromthe top plate along its outer rim; a cover member for closing over oneend of the through-hole formed in the sleeve; micro-gaps formedcontinuing between an upper-end face of said sleeve and a bottom face ofsaid rotor top plate, an inner circumferential surface of said sleeveand an outer circumferential surface of said shaft, and an inner face ofsaid cover member and an end face of said shaft; oil retainedcontinuously without interruption within said micro-gaps throughouttheir entirety; a radial dynamic pressure bearing section configuredbetween said sleeve inner-circumferential surface and said shaftouter-circumferential surface, for inducing hydrodynamic pressure intosaid oil when said rotor spins; a thrust bearing section configured onat least one of either said sleeve upper-end face or said top platebottom face, and furnished with dynamic-pressure-generating striationsfor imparting to said oil radially inward-heading pressure when saidrotor spins; herringbone grooves being contiguous pairs of spiralgrooves for generating essentially equal pressure, provided asdynamic-pressure-generating striations in said radial dynamic-pressurebearing section; and an axial support section, formed between said covermember inner face and said shaft end face, having pressure essentiallybalancing radially inward-heading pressure generated in said thrustbearing section, wherein said rotor is lifted through cooperation ofsaid thrust bearing section and said bearing section.
 19. A disk-drivedevice as set forth in claim 18: an outer circumferential surface ofsaid sleeve and an inner circumferential surface of said rotor circularcylindrical wall opposing via a radial gap; and said sleeve along itsouter circumferential surface being provided with a taper surfaceconstricting in outer diameter according as its separation from saidrotor top plate; wherein said oil is retained by a meniscus forming inbetween said taper surface and the inner-circumferential surface of saidrotor circular cylindrical wall.
 20. A disk-drive device as set forth inclaim 19, wherein: a stepped portion continuous with said taper surfaceis provided in said sleeve by recessing its outer circumferentialsurface radially inwardly; an annular member projecting radially inwardcorresponding to the stepped portion is fixedly fitted into the innercircumferential surface of said rotor circular cylindrical wall, and arotor retainer is constituted by engagement of the stepped portion andthe annular member; a micro-gap, smaller than the minimum clearance ofthe radial gap formed between the taper surface of said sleeve and theinner circumferential surface of said rotor circular cylindrical wall,is formed to function as a labyrinth seal between said annular memberalong its upper face and said sleeve stepped portion along itsundersurface.
 21. A disk-drive device as set forth in claim 18, whereinsaid radial dynamic-pressure bearing section is configured between saidshaft outer-circumferential surface and said sleeveinner-circumferential surface as an axially separated pair of radialdynamic-pressure bearings.
 22. A disk-drive device as set forth in claim18, wherein said rotor is urged in a direction toward said cover memberby axially acting magnetic force.
 23. A disk-drive device including ahousing, a spindle motor fixed inside said housing for spinningrecording disks, and an information access means for writing informationinto and reading information out from needed locations on the recordingdisks, wherein said spindle motor comprises: a shaft; a sleeve formedwith a through-hole for rotary-play insertion of the shaft; a rotorhaving a round top plate in the rotational center of which the shaft isfurnished united, and a circular cylindrical wall depending from the topplate along its outer rim; a cover member for closing over one end ofthe through-hole formed in the sleeve; a circular cylindrical casingmember fitted to said shaft over its outer circumferential surfacemicro-gaps formed continuing between an upper-end face of said sleeveand a bottom face of said rotor top plate, an inner circumferentialsurface of said sleeve and an outer circumferential surface of saidcasing member, and an inner face of said cover member and end faces ofsaid shaft and said casing member; oil retained continuously withoutinterruption within said micro-gaps throughout their entirety; a radialdynamic-pressure bearing section configured intermediarily by at leastone surface of either said sleeve inner-circumferential surface or saidcasing member outer-circumferential surface, and by said oil when saidrotor spins, and provided with, as dynamic-pressure-generatingstriations, herringbone grooves for inducing into said oil when saidrotor spins hydrodynamic pressure; a thrust bearing section configuredon at least one of either said sleeve upper-end face or said top platebottom face, and furnished with dynamic-pressure-generating striationsfor imparting to said oil radially inward-heading pressure when saidrotor spins; an axial support section, formed between said cover memberinner face and said shaft end face, having pressure essentiallybalancing radially inward-heading pressure generated in said thrustbearing section, wherein said rotor is lifted through cooperation ofsaid thrust bearing section and said bearing section; and acommunicating pathway formed in between said shaft along its outercircumferential surface and said casing member along its innercircumferential surface, for communicating said oil retained in, andenabling it to circulate between, the micro-gap formed between saidsleeve upper-end face and the bottom face of said rotor top plate, andthe micro-gap formed between said cover member inner face and said shaftand casing member end faces.
 24. A disk-drive device as set forth inclaim 23: a helical groove being formed on the outer circumferentialsurface of said shaft in a single path running from its upper-endportion to its lower-end portion; wherein fitting said casing memberover the outer circumferential surface of said shaft defines saidcommunicating pathway between said helical groove and the innercircumferential surface of said casing member.
 25. A disk-drive deviceas set forth in claim 23: an outer circumferential surface of saidsleeve and an inner circumferential surface of said rotor circularcylindrical wall opposing via a radial gap; and said sleeve outercircumferential surface being provided with a taper surface constrictingin outer diameter according as its separation from said rotor top plate;wherein and said oil is retained by a meniscus forming in between saidtaper surface and the inner-circumferential surface of said rotorcircular cylindrical wall.
 26. A disk-drive device as set forth in claim25, wherein: a stepped portion continuous with said taper surface isprovided in said sleeve by recessing its outer circumferential surfaceradially inwardly; an annular member projecting radially inwardcorresponding to the stepped portion is fixedly fitted into theinner-circumferential surface of said rotor circular cylindrical wall,and a rotor retainer is constituted by engagement of the stepped portionand the annular member; a micro-gap smaller than the minimum clearanceof the radial gap formed between the taper surface of said sleeve andthe inner-circumferential surface of said rotor circular cylindricalwall, is formed to function as a labyrinth seal between the annularmember along its upper face and said sleeve stepped portion along itsundersurface.
 27. A disk-drive device as set forth in claim 23, saidradial dynamic-pressure bearing section being configured between saidshaft outer-circumferential surface and said sleeveinner-circumferential surface as an axially separated pair of radialdynamic-pressure bearing constituents, wherein as thedynamic-pressure-generating striations in each radial bearingconstituent, herringbone-groove forming contiguous pairs of spiralgrooves for inducing into said oil when said rotor spins hydrodynamicpressure whose pressure gradient becomes axially symmetrical areprovided.
 28. A disk-drive device as set forth in claim 23, said radialdynamic-pressure bearing section being configured between said shaftouter-circumferential surface and said sleeve inner-circumferentialsurface as an axially separated pair of radial dynamic-pressure bearingconstituents, wherein as the dynamic-pressure-generating striations inat least one of either said pair of radial dynamic-pressure bearingconstituents, asymmetrically configured herringbone grooves for inducinginto said oil when said rotor spins hydrodynamic pressure actingunidirectionally in the axial direction are provided.
 29. A disk-drivedevice as set forth in claim 23, wherein said rotor is urged in adirection toward said cover member by axially acting magnetic force. 30.A disk-drive device including a housing, a spindle motor fixed insidesaid housing for spinning recording disks, and an information accessmeans for writing information into and reading information out fromneeded locations on the recording disks, wherein said spindle motorcomprises: a shaft; a sleeve formed with a through-hole for rotary-playinsertion of the shaft; a rotor having a round top plate in therotational center of which the shaft is constituted integrally, and acircular cylindrical wall depending from the top plate along its outerrim; a thrust bearing section configured on at least one of either saidsleeve upper-end face or said top plate bottom face, and furnished withdynamic-pressure-generating striations for imparting to said oilradially inward-heading pressure when said rotor spins; a radial dynamicpressure bearing section configured between said sleeveinner-circumferential surface and said shaft outer-circumferentialsurface, for inducing hydrodynamic pressure into said oil when saidrotor spins; an annular flange portion with which said sleeve isprovided wherein its outer circumferential surface flares radiallyoutward, and an annular member, projecting radially inward in a locationcorresponding to said flange portion along its underside, fixedly fittedinto an inner circumferential surface of said rotor circular cylindricalwall, a rotor retainer being constituted by engagement of the flangeportion and the annular member; wherein said annular member is harder atleast superficially than said sleeve.
 31. A disk-drive device as setforth in claim 30, wherein said annular member is formed from a ceramicmaterial.
 32. A disk-drive device as set forth in claim 30, wherein saidannular member is formed from a surface-hardened metal material.
 33. Adisk-drive device as set forth in claim 30, wherein: one end of thethrough-hole formed in the sleeve is closed over by a cover member;micro-gaps are formed continuing between an upper-end face of saidsleeve and a bottom face of said rotor top plate, an innercircumferential surface of said sleeve and an outer circumferentialsurface of said shaft, and an inner face of said cover member and an endface of said shaft, meanwhile oil is retained continuously withoutinterruption within said micro-gaps throughout their entirety; andherringbone grooves being a contiguous pair of spiral grooves forgenerating essentially equal pressure are provided asdynamic-pressure-generating striations in said radial dynamic-pressurebearing section, an axial support section is formed between said covermember inner face and said shaft end face, having pressure essentiallybalancing radially inward-heading pressure generated in said thrustbearing section, wherein said rotor is lifted through cooperation ofsaid thrust bearing section and said bearing section, meanwhile saidrotor is magnetically urged in a direction axially opposing its liftingdirection.
 34. A spindle motor as set forth in claim 30: said flangeportion along its outer circumferential surface and said rotor circularcylindrical wall along its inner circumferential surface opposing via aradial gap; and said flange portion along its outer circumferentialsurface being provided with a taper surface constricting in outerdiameter according as its separation from said rotor top plate; whereinsaid oil is retained by a meniscus forming in between said taper surfaceand the inner-circumferential surface of said rotor circular cylindricalwall, meanwhile a micro-gap, smaller than the minimum clearance of theradial gap formed between the taper surface along said flange portionouter circumferential surface and the inner circumferential surface ofsaid rotor circular cylindrical wall, is formed to function as alabyrinth seal between said annular member along its upper face and saidflange portion along its undersurface.